Lathe



G. D. SUNDSTRAND ET AL LATHE Filed Sept. 13, 1930 10 Sheets-Sheet 1 Oct. 18, 1932. s. p. SUNDSTRAND ET AL 1,383,082

LATHE Filed Sept. 15, 1930 1Q Sheets-Sheet 2 jandsfram Oct. 18, 1932.

G. D. SUNDSTRAND ET AL LATHE Fil'ed Sept. 13, 1930 10 Sheets-Sheet 3 Oct. 18, 1932. I s. D.-SUNDSTRAND ETAL. 1,383,082

Oct. 18, 1932. s. D. SUNDSTRAND ET AL 3,

LATHE Filed Sept. 15, 1950 10'Shoets-Sheet 7 I IHH IWW. W HHMEEHQM r Oct. 18, 1932. e. D."'SUNDSTRAND ETAL 1,383,082

LATHE Filed Sept. 13, 1930 10 Sheets-Sheet 8 .nKH

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Oct. 18, 1932.

c! D. SUNDSTRAND #:1- AL LATHE Filed Sept. 13, 1930 10 Shoots-Sheet 9 ll lllll l Ill... 1 Aw NNN Oct. 18,1932

10 Sheets-Sheet 10 (Figs.-

Patented a. 18, 1932 UNITED STATES PATENT- OFFICE GUSTAF DAVID sunns'rnnnn, nncnnsnn, mm or nocnoan, ILLnmrs, 3'! 21min. sunnsrnann, EXECUTBIX, or nocxronn, rumors, AND JOHN r. BENNER, or

ROGKFORD, ILLINOIS, ASSIGNOBS 'IO 8U FORD, ILLINOIS, A. CORPORATION 01 ILL NDSTRAII'D CHINE TOOL 00., OF ROCK- INOIB LATHE Application filed September 13, 1880. Serial Io. 481,884.

The invention relates to lathes and more particularly to automatic lathes adapted to perform a plurality of operations.

The general object of the present invention is to provide an automatic lathe of a universal character as distinguished from special single purpose machines, adapted to operate with a speed and accuracy equal to such single purpose machines and capable of convenient and rapid set up for any one of a large variety of automatic cycles.

Another object is to provide a lathe having improved and simplified cam actuating mechi anism for the movable supports arranged for convenient and accurate adjustment whereby to vary the relative timing of the working strokes ofthe sup orts.

Another object is to provide a lathe em;- bodying a novel mechanism for relieving the front tools at the beginning of the carriage return stroke.

Another object is to provide such a. lathe embodying a new and advantageous control mechanism.

Another object is to provide a lathe'embodying a control mechansm havin an improved safety stop device whereby t e lathe operation may be stopped by a rapid and easily accomplished movement of a conveniently positioned control lever.

Other ob'ects and advantages will become apparent rom the following description taken in connection with the accompanying drawings in which:

Fig. 1 is a front elevational view, partially in section, of a lathe embodying the invention in its preferred form. Fig. 2 is an elevational view of the headstock end of the machine shown in Fig. 1.

Fig. 3 is an elevational view of-the tailstock end of the machine, the tailstock being shown indotted outline- Fig. 4 is a plan section showing the headstock gearing, the section being taken along the line 44 of Figs. 2 and 3.

- anot Fig. 5 is a fragmental plan section taken along the line 5-5 of Fig. 2 and showing a part of the headstock gearing.

Fig. 6 is a fragmental plan section taken along the line 66 of Fig. 3 and showing er part of the headstock gearing.

Fi 7 is a plan section taken alon the line 7 of Figs. 11 and 12 and showlng a part of both the feed and traverse gearing for the tool supports.

Figs- 8 and 9 are fragmental plan sections taken along the lines 8-8 and 99 respectively of Flg. 12.-

Fig. 10 is a fragmental vertical sectional viewtaken along the line 10-10 of Fi 12.

Fig. 11 is an enlarged fragmental en elevational view of the headstock end of the machine as viewed from the line 1111 in Fig-12 and showing in dotted outline the feed and traverse gearin Fig. 12 is an enlargekf fragmental front elevational view as seen from the line 1212 of Fig. 11. and showing the feed and traverse gearing in dotted outllne.

Fig. 13 is a diagrammatic view of the headstock gearing.

Fig. 14 is a diagrammatic view of the feed,

traverse and control gearing.

Fig. 15 is an enlarged fragmental elevational view of the headstock end of the machine showin a part of the rear cross slide actuating me ianism.

Fig. 16 is a fragmental vertical sectional view taken along the line 16-46 of Fig. 15 and showing the actuating cam of the rear cross slide actuating means.

Fig. 17 is a fragmental view taken along the hue 17-17 of Fig. 15 and showing the cam follower and connecting rod of the rearicross slide actuating means.

Fig. 18 is a fragmental vertlcal section taken along the line 18--i8 of Figs. 1, 19 and p 20 and showing the rear cross sli nd a part of itsactuating mechanism.

v Fig. 19 is an elevational view of the rear tending ways 12 and upon the forward pair of ways 12 a front car-v carriage and cross slide as viewed from the left in Fig. 18.

Fig. 20 is a plan view of the rear carriage and cross slide.

Fig. 21 is a fragmental vertical sectional view of the front carriage and cross slide taken along the line 21- -21 of Figs. 1 and 22.

Fig. 22 1s a plan section taken along the line 22-22 of Fig. 21 showing the relieving mechanism.

Fig. 23 is a plan view of the front carriage and cross slide.

front carriage and cross slide.

Fig. 25 is an enlarged fragmental elevation of the control mechanism as viewed from the left in Fig. 1.

Fig. 26 is an enlarged front elevational View of the control mechanism.

. Fig. 27 is a cross sectional view of the main control valve taken along the line 27--27 of Fig. 25.

Fig. 28 is a cross sectional view showing the mounting of a manual control handle an taken along the line 28-28 of Fig. 26.

Fig. 29 is a diagrammatic view of the control mechanism showing the hydraulic circuits.

For purposes of disclosure the preferred form of the invention is illustrated in the drawings and will hereinafter be described in detail as applied to a particular form of lathe, but it is to be understood that this disclosure is not intended as a limitation of the invention to this type of machine tool, it being contemplated that various changes might be made by those skilled in the art to adapt the invention to other types of tools without departing from the spirit and scope of the 'invention as defined by the appended claims.

In the preferred form chosen for dis closure herein, the invention is illustrated as embodied in a lathe having a bed 10 with an upstanding headstock 11 at one end thereof.

Between the headstock 11 and the other end of the bed a plurality of longitudinally ex- 13 are provided and riage 14 is slidably mounted. The front carriage 14 has a cross slide 15 mounted thereon for movement transversely Upon the rear pair of ways 13, a rear carriage 16 is mounted for adjustment longitudinally of the lathe and carries a transversely movable cross slide 17, arranged to move at an angle to the horizontal. In the headstock 11 a work spindle 18 is rotatably supported in longitudinally spaced bearings. A rotatable tailstock spindle 19 is mounted in alincment with the headstock spindle in a frame 20 which is longitudinally adjustable upon the two adjacent ways12 and 13 and the spindle 19 may be longitudinally adjusted in the frame 20 by conventional means including a hand wheel 21.

Fig. 24 is a front elevational view of the pulley 26 (Fig' ,intermeshing gears of the lathe.

H eadst ock gearing comprises a main shaft 23 mounted in the headstock 11 parallel to the spindle 18 and having a ulley 24 thereon which may be connected by means of a belt 25, (Fig. 2) to a 2) fixed on the motor shaft. From the main shaft 23, two differently speeded geared connections are provided to the headstock spindle 18, the two gear trains being adapted to be selectively connected to the spindle and each train preferably embodying a pair of conveniently positioned pick-off gears for varying the relation of the two spindle speeds. As illustrated herein the high speed gear train includes a gear 30 loosely mounted on the shaft 23 and arranged to drive a shaft 31 (Fig. 5) through the medium of intermediate gears 32 and 33. The shaft 31 is also mounted parallel to the spindle 18 and projects through the left hand and of the headstock 11 to receive a. pick-off gear 34 (Figs. 2 and 5) which is arranged to mesh with a complementary pick-off gear 35 (Figs. 2 and 4) allel shaft 36. The shaft 36 which extends entirely through the headstock 11 and is common to both the high speed and low speed gear trains, carries a gear 37 which meshes with a gear 38 fixed on the headstock spindle 18. a The low speed gearing from the main shaft 23 to the headstock spindle 18 includes a gear 40 loosely mounted on the-shaft 23 in spaced relation to the gear 30 and arranged .to drive a shaft 41 (Fig. 6) through the medium of 42 and 43. The shaft 41 projects through the right hand end of the headstock 11 in spaced relation to the end of the shaft 36 and carries a pick-off gear 44 arranged to mesh with a complementary pick-off gear 45 secured on the projecting end of the shaft 36. Between the two gears 30 and 40, a clutch member 46 is splined on the shaft 23 and at its opposite ends has a pair of friction clutches 47 and 48 for engaging selectively either the high speed or low speed gear train.

Feed shaft actuating mechanism The front carriage and cross slide and the rear cross slide are arranged to be actuated at feed speeds from the spindle 18 and at traverse speeds directly from the motor 22. The feed and traverse gearing is best illustrated in Figs. 7 to 12 and 14. The feed and traverse drives include a common feed shaft 54 extending transversely of the bed 10 beneath the headstock which is driven at feed secured on the end of a parspeeds from the spindle and at traverse speed directly from the motor 22.

The traverse drive to the feed shaft 54 includes a shaft 55 (Figs. 7 and 14) mounted in the base so as to extend longitudinally thereof and connected to the shaft of the motor 22 by sprockets 56 and 57 and a chain 58 (Fig. 14). On the shaft 55 within a gear box 59 is a gear 60. The gear 60 engages and drives a gear 61 on a parallel shaft 62 which extends through the wall of the gear box 59 and carries a worm 63 arranged to engage a worm wheel 64 (Figs. 11 to 14) loosely mounted on the feed shaft 54. To cause rotation of the feed shaft 54 at the traverse speed in aforward direction the worm wheel 64 may be clutched to the shaft by a traverse clutch element 65 having teeth '66 on one end thereof for engaging clutch I teeth on the worm wheel 64. At its other end the traverse clutch 56 has teeth 67 p for engaging corre; sponding teeth on another loosely mounted the feed shaft 54.

The shaft 70 projects into the gear box 59 and carries a gear 71 meshing with a gear 72 fixed on the shaft 62 so that the shafts 62 and 70 are driven in reverse directions; The traverse clutch 65 has a neutral position so that the feed shaft 54 may be actuated independently of the traverse drive.

The feed drive for the feed shaft 54 is taken from the spindle 18 through a sprocket 75 (Figs. 1 and 14) fixed on the spindle 18 and engaging a chain 76 mounted within a casing ,7 7 on the headstock end of the base. At its lower end the chain 76 engages a sprocket 78 mounted ona horizontal shaft which also carries a second sprocket 79. An

endless chain 81 enga es the sprocket 79 and drives a sprocket 82 %Figs. 1 and 7) carried on the projecting end of a horizontal shaft 83 journaled in the bed 10.

Within the bed 10 and outside of the gear box 59, the shaft 83 is coupled at- 83 to a stub shaft 84 projecting into the gear box and carrying a gear 85. A similar stub shaft 86 projecting into and j ourn aled in the gear box 59'carries a gear 87 which is driven from the gear 85 through an intermediate gear 88 mounted within the gear box 59.

At its outer end the stub shaft 86 iscou led at 86 to a shaft 90, the splined end of w ich projects through the left end of the bed 10 to receive a pick-01f gear 91 (Figs. 7 and 14) A companion pick-01f gear 92 on a parallel shaft 93 meshes with the gear 91 and the shaft 93 is coupled at 93" to a horizontal shaft 94.. The shaft 94 carries a worm 95 in driving engagement with a worm, wheel 96 (Figs. 11, 14 and 29) which is loosely mounted on the feed shaft 54 and may be connected thereto by means of a splined feed clutch 97.

Thus by selective engagement of the feed clutch 97, the rapid approach clutch 66 or the rapid return clutch 67, the feed shaft 54 may be caused to rotate at feed or traverse speed in a forward direction or at a traverse speed in a reverse direction. It will be seen that the feed speed is capable of a wide range of variation since change gears 34, 35 and 44, 45 are provided in the spindle drives as well as change gears 91, 92 in'the feed drive between the spindle and the feed shaft 54.

Clutch actuating means In the present embodiment the feed and traverse clutches as well as the spindle speedchange clutch 46 are hydraulically actuated. As illustrated herein the clutches are shifted toengaged positions by means of pressure fluid operated piston and cylinder devices, against'the action of springs whichtend normally to maintain the clutches in their disengaged positions. As shown in Fig. 29, the feed and traverse clutch actuating means comprises a tubular member 00 which is supported adjacent and arzille to the feed shaft 54 and hasa plu ality of transverse walls 101 forming cylinders 102 and 103 in which pistons 104 and 105 are slidably mounted. The pistons 104 and 105 have laterally projecting arms 106 and 107 projecting through 'the walls of the cylinders, the arm 106 ehgaging the feed clutch 97 while the arm 107 engages the traverse pair of pins 111. The PlIlS 111 extend through plugs 112 in the ends of the piston and engage the end walls 101 of the cylinder so that the piston 105 is normally urged to a central position in the cylinder, in which position the traverse clutches are disengaged. To engage the clutch 66 to cause rapid approach movement of the feed shaft 54, pressure fluid is admitted to one end of the cylinder through a port 114, while the rapid return clutch 67 may be engaged by admitting ressure fluid to the other end of the cylin' er through a port 113.

A similar piston and cylinder device is provided for actuating the spindle speed cha clutch 46. As shown in Figs. 4 and 2 device 'consistsofa cylinder havin ton 121 slidably mounted therein. 1 ton 121 has an arm 122 projecting a slot in the cylinder and engaging the 46, so as to form av shifting yoke there Within the piston 121 a spring device 123 is mounted, similar to that embodied in the pis- III '7 ton 105 abovedescribed, and arranged noror the other, pressure fluid connections may be provided to the opposite ends of the. cylinder 120 as hereinafter more fully described.

Rear cross slide actuating mechanism As hereinbefore mentioned, the feed shaft 54 is arranged to actuate the front carriage 14 as well as the front and rear cross slides 15 and 17. Such actuation is preferably obtainedby means of a plurality of somewhat similar cam devices driven from the feed shaft 54, one cam being provided for actuating each cross slide and a third cam being provided for longitudinally reciprocating the front carriage 14. As illustrated herein, the cams are in the form of cylinders or drums 130,131,132 (Figs. 11, 12 and 16) mounted in the bed 10 adjacent to the left end thereof for rotation about longitudinally extending horizontal axes. Preferably each cam drum is ad ustably connected to the feed shaft 54 to permit variation of the timing of the working strokes ofthe various tool supports and is also adjustably connected to its particular support so as to permit of adjustment of the position of the working stroke with relation to the bed.

The mounting of the rear cross slide cam 130 is shown in detail in Fig. 16 and comprises a pair of axially alined sleeves 133 and 134 surrounding a shaft 135 the sleeves being rotatably supported in bearings 136 in the bed 10 in such a manner that the left hand'end of the shaft 135 and the sleeve 133 project outside of the bed. The cam 130, which is tubular in form and is held in fixed longitudinal position in the bed, surrounds and is slidably keyed to the sleeve 133. Ro tation is imparted to the cam drum 130 through the sleeve 134 and to this end a plurality of interengageable teeth 137 (Fig. 16)

- are provided on the adjacent ends of the sleeves 133 and 134. The teeth 137 are maintained in operative engagement by the shaft 135, a collar 138 on the right end thereof and a nut 139 threaded on the projecting left end of the shaft. Thus by loosening the nut 139 the sleeve 133 may be moved outwardl of the bed to disengage the clutch teeth 13% on the sleeves 133 and 134 so that the sleeve 133 and the cam 130 may be rotated freely for purposes of angular adjustment. To facilitate such adjustment, the projecting left end of the sleeve 133 is squared as at 140 (Fig. 15).

As shown in Figs. 11, 12 and 14, the rear cam 130 is driven from the feed shaft 54 by means including a pair of change gears 141 and 142, the gear 141 being secured on the splined forward end of the feed shaft 54 while the gear 142 is secured on a parallel shaft 143 extending toward the rear of the bed. At its rear end the shaft 143 carries a gear 144 which, through gears 145 and 146 drives a horizontal shaft 147. Upon the shaft 147 a worm 148' is carried which engages a worm wheel 149 splined to the sleeve 134. Thus when the worm wheel 149 is rotated, such rotation will be transmitted through the sleeve 134 and the clutch teeth 137 to the sleeve 133 which through its splined connection will cause rotation of the cam 130. If desired the shaft 147 may be provided with a gear 150 for driving suitable attachments which may be mounted upon the lathe. 7

For the purpose'of transmitting movement from the cam 130 to the rear cross slide 17 the cam has a spiral groove 151 formed therein with dwell portions 151 at each end thereof. A follower 152 engages the cam groove 151 and is carried by a slide 153 of rectan ular cross section mounted in the bed for movement parallel to the axisof the cam drum. Extending longitudinally through the slide 153 is a connecting rod or shaft 154 rotatably mounted in the slide and fixed against longitudinal displacement relatively thereto. The connecting rod 154 extends longitudinally of the bed and is screw threaded into a slide 155 mounted in the lower por; tion of the rear carriage 16 for longitudinal reciprocation therein. By rotation of the shaft 154 the connection between the cam drum 130 and the slide and to facilitate such adjustment the end 156 of the connecting rod 154 projects beyond the left end of the slide 153 and is squared as shown in Figs. 15 and 17.

When the slide 155 is reciprocated a corresponding reciprocation of the roar cross slide 17 is obtained by means shown in Figs. 18 and 20. v crank formed by a shaft 160 mounted in the carriage 16 for rotation about an axis perpendicular to the plane of movement of the cross slide and carrying arms 161 and 162 at the upper and lower ends thereof respectively, the upper arm 161 carrying a pin 163 engaging in a transverse slot 164 formed in the cross slide 17 At its outer end the lower arm 162 carries a downwardly projecting pin 165 which may engage a transverse cam slot 166 formed in the slide 155 (Fig. The arrangement of the bell crank is such that, when the slide 155 is movedtoward the tailstock end of the machine (that isupwardly as shown in Fig. 20), the cross slide willbe moved toward the work and after a given range of movement in this direction the pin 165 moves out of the slot 166 and engages a cam surface 168 on the side of the slide 155 so that during conti'nned movement of the slide in the same direction the cross slide will be held stationary in its innermost position. In order that the pin 165 may be directed into the transverse slot 166 This means comprises a hell 155 may be adjusted from the slide 155 at the of the slot 166.

- carriage cam 131 is preferably of the sameupon return movement of the slide 155 a hook shaped member 169 projects rearwardly left or far edge Front carriage actuating wwchaniam As hereinbefore pointed out, the front form, has the same adjustable features and is mounted in the same manner as the cam 130, the position of the cam 131 being indicated in Figs. 2 and 11. A slide 175 similar to the slide 153 is mounted above the cam drum 131 (Fig. 11) and carries a roller 176 engaging the cam, the slide 175 beingabutment with one of the end plates 180 or 181, to move the front carriage 14 longitudinally of the bed.

The cam 131 is driven from the feed shaft 54 through a gear 182 on the feed shaft, an intermediate gear 183 (Figs. 8, 12 and 14), engaging a gar 184 fixed on a horizontal shaft 185, and a worm 186 on shaft 185 engaging a worm wheel 187 fixed on the end of the cam 131. The other end of the shaft 185 projects from the front of the bed 10 and carries a handwheel 188 through which the feed shaft 54 may be manually actuated when the feed and traverse clutches are disengaged.

Front cross slide acbuatz'ngpweham'sm The cam 132 for actuating the front cross slide 15 is mounted in the bed 10 parallel and ad acent to the cam 131 (Figs. 2, 11 and of the-front carriage 14 adjacent to the bar 17 8 and above the su portin plate 179 and is arranged to slide ongitu inally through the end plates 180 and 181. The longitudinal reciprocation of the slide 198 causes transverse reciprocation of the front cross slide 15 through a .bell crank device similar to that used in the rear cross slide actuating mechanism as shown in Figs. 21 to 24. This device comprises a vertical shaft 200 mounted in the carriage 14 and carrying arms 201 and 202 at its upper and lower ends respectively. The upper arm 201 is engaged with the cross slide 15 b a pin and slot connection so that upon osci lation of the shaft 200 the cross slide will be actuated. At the outer end of the lower arm 202 a boss 203 projects down-' wardly and carries a pin 204 (Fig. 21), adapted to engage a transverse slot 205 (Fig. 23) formed in the upper side of the slide 198.

- Thus when the pin 204 is engaged with the slot 205 and the slide 198 is moved to the right as shown in Fig. 23, the arm 202 will be moved in a counter-clockwise direction so as 'to advance the cross slide 15. As such movement of the slide continues the pin 204 will move out of the slot 205 and the boss 203 will engage and slide along a cam surface 206 (Figs. 21 and 23) on the slide 198 so that the cross slide will remain stationary. In order to direct the pin 204 into the transverse slot 205 upon return movement of the slide 198, a hook-1i ke projecting member 207 is mounted on the slide 198 as shown in Fig. 32.

As herein shown, the lathe embodies means for withdrawing the front tools at the beginning of the carriage return stroke so that they do not mar the finished work piece and this means is preferably connected to and operated by the front carriage actuating means and acts through the cross slide actuating mechanism to obtain the desired movement of the. front cross slide. To this end the member 17 8 has a slight lo'st motion with respect to the carriage 14 during which it is ineffective to move the carriage and is arranged during such movement to cause the cross slide 15 to be actuated in accordance with the direction of movement of the member 17 8.

The member 17 8 (Figs. 21 and 22) has an angula-rly extending vertical surface 210 formed along the lower edge thereof engaging a complementary surface 211 formed on the carriage 14 so that during the non-car ria-ge propelling movement of the member 178 from the position shown in Fig. 22 into abutment with the plate 181, the member 178 will be moved to the right, that is toward the front of the lathe. It will be noted in Fig. 21 that the forward surface of the member 178 engages the rear side of the boss 203, the other side of which engages the cam surface 206 of the slide 198, and in order to permit transverse movement of the inember 178, the slide 198 is held in position by means which may be released when such transverse movement is desired.

As illustrated in Fig. 22, this means comprises a wedge 212, mounted on the forward side of the slide 198 for limited sliding movement longitudinally of the slide 198 and arranged to act against a rearwardly facing angular surface 213 formed in the carriage 14. Thus, as shown in Fig. 22, when the wedge. 212 is moved toward the tailstock end atingarm 202 is established.

of the machine (upwardly in Fig. 22) the slide 198 will be heldagainst transverse displacement. For the purpose of moving the wedge 212 to its inoperative position when the relieving action is desired, a lever 214 is positioned in a recess in the bottom plate 179 and is pivoted at its mid point to the plate. At its opposite ends the lever 214 has upstanding pins 215, one of which projects into a suitable recess in the bottom of the member 178, while the other pin 215 projects into a transverse slot 2l6 in the bottom of the wedge 212. Thus, when themember 17 8 is moved toward the tailstock end of the machine the lever 214 will retract the wedge 212 so as to" permit transverse displacement of the slide 198, and the engagement of the angular surfaces-210 and 211 will cause the member 17 8 tomove the boss 203 forwardly of the machine. This causes a slight clockwise movement of the shaft 200 (Fig. 23) and therefore withdraws the tools a slight distance away from the work.

When the member 178 is moved in the opposite direction, the lever 214 moves the wedge 212 back to its operative position (Fig. 22) so that the normal operative relation between the slide 198 and the-cross slide actu- Hydraulic circuits and manual control actuating the clutches and a unitary control 7 valve is preferably provided for all of the piston and cylinder devices. As herein shown a tubular valve casing 220 (Figs. 25, 26, 27 and 29) is mounted on'the bed 10 within a frame 221 which is positioned in front of the headstock 11. The valve casing 220, in the present case, extends transversely of the machine and has a valve member 222 slidably mounted therein. Within the bed 10, an oil pump 223 is mounted, arranged to be driven from the motor 22 whenever the motor is in operation by suitable means (not shown) and operable to pump fluid under pressure from a supply tank 224 through a supply conduit 224 to the valve casing 220. From the valve casing 220 the pressure fluid is distributed to the various piston and cylinder devices in accordance with the longitudi nal position of the valve member 222with1n the casing;

In Fig. 29, an exempla hydraulic circuit is illustrated, this circuit ing designed for work on which two difierent spindle speeds ma be used as the o ration rogresses. In such an. operation e-spind e may remain 'stationar during the rapid approach movement of t e supports an as soon as the feeding movement of the supports has started the spindle ma be rotated at comparatively slow speed. ile being rotated at such a slow speed the larger diameter cuts may be made and when these cuts have been, completed, the spindle speed may be increased. As soon as the cutting operation has been completed the spindle is preferably-stopped and the supports retracted at rapid traverse speed.

The valve 220 is designed for such a working cycle and has five longitudinally spaced positions, arranged in the following order from front to rear: (1) rapid approach, hereinafter designated as R. A., (2) spindle and feed at low s eed, hereinafterdesignated as F, (3) spindle and feed at high speed, hereinafter designated as F, (4) neutral, designated as N, and (5') rapid return, hereinafter designated as R. R. The pressure fluid. supplied to the valve casing is conducted through a bore 225 in the valve member 222 to a plurality of radially extendin ports 226 from which the fluid is conducte to the various piston and cylinder devices in accordance with the position of the valve.

When the valve 222 is in its rapid approach position, the ports 226 register ,with an annular groove 227 (Fig. 29) and the fluid is conducted from the groove 227 through a conduit 228 which is connected to the port 114 of the cylinder 103 so as to engage the raga? approach clutch 66.

en the valve 222 is moved rearwardly to its next or F position, the valve ports 226 register with another annular groove 227 which is 120 by a conduit 230 so as to engage the low speed spindle clutch 48. The pressure fluid from the groove 227 also engages the feed clutch 97, preferably after the spindle has started to rotate. To this end a conduit 231, extending from the port 109 of the feed clutch cylinder 102, is connected to the side ofthe cylinder 120 at 232 'so that the fluid from the cylinder is not admitted to the cons duit 231 until the spindleclutch 48is engaged. By this arran ement the feed clutch operation is timed wit respect to the spindle clutch, so that the feed clutch is disengaged before the disengagement of the spindle clutch whereby to cause the cut to be cleared. In the F position of the valve 222, the ports 226 communicate with an annular groove 227 which is connected with the other end of the cylinder 120 by a conduit 233 so as to cause engagement of the high speed spindle clutch 47. For the purpose of engaging the feed clutch when the valve is in its F position a conduit 234, extending from the port 109 of the feed clutch cylinder 102. is connected at 235 to the side of the cylinder 120 in the same manner as the conduit 231 so as to provide for the same interlocked actuation of the spindle and feed clutches. a

When the valve 222 is in its neutral position, the ports 226 register with another annular groove 227 d from which the pressure fluid connected to one end of the cylinder 1,ssa,osa

is by-passed to the supply tank 224 through apipe 236.

In the rapid return position of the valve an annular groove 227 re isters with the ports 226 and the pressure uid passes from the groove 227 through a conduit 237 which is connected to the port 113 of the cylinder 103 so as to engage the rapid return clutch 67.

The present embodiment of the invention provides for either manual or automatic operation. For the pur )cse of manually actuating the-valve mem r 222, a rack 240 is formed on the underside of a slide bar 239 (Figs. 25 and 29) mounted in the frame 221 ccaxially with and connected to the valve 222. A shaft 241 (Fig. 25) extending transversely from the valve member has a pinion 242 at one end thereof engaging the rack 240. The shaft 241 is rotatably journaled in the frame member 221 and has a beveled gear 243 (Fig. 26) at the other end thereof engaged by a beveled gear 244 (Fig. 28) which is connected to the handle 245 mounted in an angular position on the outside of the frame member 221. Thus, by moving the handle 245 about its pivotal axis, the valve member 222 may be shifted from one position to another.

Automatz'ccontrol means shaft 250, and gears 251 and 252 (Figs. 9 and In the present embodiment of the automatic control means, the valve member 222 is constantly urged rearwardly in the valve'cas ing by a spring 254 (Figs. 25 and 26) and is restrained against such movement by means including the control member 246. To this end the control member 246 is preferably of drum-like form, stepped as shown in Figs. 25 and 29 to form a plurality of annular portions or surfaces 255, 255, 255 and 255, of different diameters and also to provide a plurality of forwardly facing annular surfaces or abutments 256 256", 256 and 256. For engagement with any one of the abutments 256, a detent 257 is mounted in the forward end of the horizontal bar 239 for sliding movement transversely of the-bar 239 and radially with respect to the stepped control drum 246 (Figs. 25 'and 26). As hereinbefore mentioned, the bar 239 is mounted in the frame 221 in alinement with the valve member 222and is connected to the valve so head 259 having a side surface 260 adapted to abut any one of the vertically positioned annular abutments 256 of the control drum.

The head 259 also has an end surface 261 adapted to ride upon any one of the periphoral surfaces 255. By this arrangement the surface 256 with which the detent is engaged Thus when the valve 222 is moved bymeans of the manual control handle 245 and the detent 257 is positioned over the surface 255, the detent 257 will drop downwardly until the surface 267 thereof engages the annular surface 255*. The valve 222 will then be in its rapid approach position and will be maintained in this position by the engagement of. the surface 260 of the detent with the abutment 256 also designated as R. A. in Figs. 25 and 29. Asso'on as the valve 222 is moved to its rapid approach position, as above described, the feed-shaft 54 will start to rotate and will causea corresponding rotation of the control drum 246 in the direction indicated by the arrow in Fig. 26.

In order to lift the detent 257 automaticah 1y at the proper time, an L-shaped trip dog 262 is secured on the control drum 246 by means of a bolt extending through one leg of the trip dog and engaging an annular T- slot 263 formed in the forward end of the control drum. The other leg of the trip dog 262 extends rearwardly'across the surface 255 as shown in Fig. 25 and is beveled as shown in Fig. 26 to provide a sloping cam surface 264 which gradually raises the detent 257 as the drum rotates. When the detent has been raised to the level of the surface 255, it is drawn rearwardly by the abutment 256 (also designated as F1) on the control drum. When the plunger is in this tion so that the spindle is rotated at its low speed and the tool supports are advanced at a corresponding feed speed.

A similar trip dog 265 is provided on the control drum 246 overlying the surface 255" and serves to lift the detent 257 over the next step of the drum so that it may engage the annular abutment 256, also designated. as F in Figs. 25 and 29. The valve 222 is then in its third position in which the high speed spindle drive is effective andthe tool supports are advanced at a corresponding feed speed.

Upon the completion of the cutting operation, a reverse dog 267, positioned on the control drum so as to overlie the surface 255 (Fi 25) raises the detent 257 so that it may be rawn rearwardly into engagement with the abutment 256, also designated as BB in 1,10 position the valve 222 is in its low speed position and causes a rapid return movement of the tool supports with a corresponding reverse rotation of the control drum 246. When the tool supports have reached their initial positions,a stop dog 268 secured on the control drum 246 moves the detent forwardly until the valve 222 is in its neutral position. As herein shown the trip dog 268 is bolted to a Tfcl'ot 269 in the rear surface of the drum 246 and-projects forwardly over the edge of the drum'so as to engage the head 259 of the detent. x

Safety stop device The lathe preferably embodies means whereby the control valve 222 may at any time be moved quickly and with certainty from any of its operative positions directly to and not beyond, its neutral position, so as to stop the operation of the lathe. This means acts as a safety stop and enables the operator, in case of an emergency,-to stop the machine by a simple and easily performed movement. In the present case, the safety stop means includes a manually shiftable lever 27 5 having valve actuatin means associated therewith whereby a unidirectional movement of the gaged lever 27 5 as far as it is permitted to go in that direction will move the control valve to and not beyond its neutral position from any of its other positions even though there are other operative positions beyond the neutral position. As herein shown in Figs. 25 and 26, thelever 275 is fixed on the projecting end of a horizontal shaft 276 which is rotatably mounted in a pair of spaced upwardly projecting brackets 277. Between the two brackets, an arm 278 is fixed on the shaft 276 so as to project forwardly therefrom for connection with the detent 257. To provide such a connection the forward end of the arm 278 is bifurcated as at 279 so as to embrace the opposite sides of a transversely extending bar 280 secured on the detent 257. In the opposite sides of the bar 280 horizontal grooves 281 are formed and these grooves are slidably enby blocks 282 pivotally secured on the bifurcated ends of the arm 278.

Thus by moving the lever 275 rearwardly the detent ment with the drum 246 and means is provided which cooperates with the detent 257 in its upward movement to cause it to be moved parallel to the axis of the valve 222 until the valve is in its neutral position. This means as herein shown comprises a member 285 sup- Sorted by the brackets 277 and having a ownwardly opening conical recess 286 adapted to coperate with the conical upper end 2870f the detent 2 57 to stop the movement of the detent at the proper point. Thus if the valve is in its rapid approach or one of 257 may be raised out of engage-.

upwardly so that the conical end 287 engages the forward sloping surface of the recess 286, the spring 254 acting to draw the detent toward the neutral position of the valve as the head 259 of the detent is raised out of engagement with the annular abutments, while if the valve is in its rapid return position, the detent will be moved upwardly to engage the rear surface of the recess 286. In either case the continued upward movement of the detent by means'of the lever 275 will'cause the detent to be moved in a horizontal direction so as to. bring the valve 222 to its neutral position.

The safety stop lever 275 is also adapted for use in shifting the valve 222 to its rapid approach position to initiate the automatic cycle of support movement. For this purpose, as shown in Figs. 25, 26 and 29, a toggle device is employed. The toggle device shown consists of a pair of links 290, one of which is loosely pivoted on the shaft 241 while one end of the; other link is pivoted at 291 on the outer end of the slide 239. The other ends of the two links 290 are pivoted together by means of a bolt or stud 292 which projects laterally from the links and under the arm 278 of the lever 27 5'. For cooperation with the projecting end of the bolt 292, a cam surface 293 is formed on the lower side of the arm 278 so that when the lever 27 5 is moved forwardl ,the bolt 292 will be engaged so as to exten the toggle links 290 and move the valve 222 to its forward or rapid approach position. A lug 294 on the arm 27 8 serves to engage the frame 221 and limit such movement of the valve 222.

We claim as our invention:

1. A. lathe having, in combination, a bed, movable tool supports on said bed, a rotat able headstock spindle, a prime mover, two differently speeded driving connections from said prime mover to said spindle including a common clutch element, a pressure fluid actuat'ed piston and cylinder device for shifting said clutch element, a feed shaft rotatably mounted in said bed and operatively connected to said supports, a constant speed revers-. ible traverse drive directly from said prime mover to said feed shaft and including a reversing clutch, a pressure fluid actuated piston and cylinder device for selectively engaging said clutch to obtain forward or reverse rotation of said feed shaft, a driving connection from said spindle to said feed shaft for rotating said shaft at a feed speed determined by the speed of said spindle and including a feed clutch, a pressure fluid actuated piston and cylinder device for controllin said feed clutch, valve means for contro ling the operation of said piston and cylinder devices, and means driven in unison with said feed shaft for controlling the position of said valve means.

2. A lathe comprising, in combination, a bed, a headstock spindle rotatably mounted its feed positions,the detent 257 will be moved thereon, movable tool supports mounted on the bed, a prime mover, a high speed'drive and a low speed drive from said prime mover to said spindle, each of said drives including a pair of alterable change gears and a clutch, pressure fluid actuated means for selectively engagingsaid clutches, a feed shaft operatively connected to said supports, a reversible traverse driving connection between said prime mover and said feed shaft including a traverse reversing clutch, pressure fluid actuated means for engaging said traverse clutch to rotate said feed shaft in forward or reverse directions, a driving connection between said spindle and said feed shaft for rotatin said shaft at a feed speed, determined' y the speed of the spindle, said feed drive including a pair of alterable change gears and a feed clutch, pressure fluid actuated means for engaging said feed clutch, and valve means for controlling the operation of said pressure fluid actuated means.

3. A lathe comprising, in combination, a bed, a headstock spindle rotatably mounted thereon, movable tool supports mounted on the bed, a prime mover, a high speed drive and a low speed drive from said primemover to said spindle, each of said drives including a pair of alterable change gears and a clutch, pressure fluid actuated means for selectively engaging said clutches, a feed shaft operatively connected to said supports, a reversible traverse driving connection to said feed shaft including a traverse reversing clutch, presstock spindle rotatably trolled means for sure fluid actuated means for engaging said traverse clutch to rotate said feed shaft in forward or reverse directions, a -drivin connection between said spindle and said feed shaft for rotating said shaft at a feed speed determined by the speed of the'spindle, said feed drive including a feed clutch, pressure fluid actuated means for engaging said feed clutch, a source of pressure fluid, valve consupplying pressure fluid to said spindle clutch engagin means, a conduit for conducting pressure uid from said spindle clutch engaging means to the feed clutch engaging means, and valve controlled means for conducting pressure fluid to said traverse clutehengaging means.

4. A lathe comprising, in combination, a bed, movable tool supports thereon, aheadmounted on the bed, a feed shaft operatively connected to said supports, means deriving power from said prime mover operable to rotate said shaft in forward or reverse directions at a traverse rate, two differently a prime mover,

, speeded driving connections between said prime mover and said spindle, said connections including a common clutch element shiftable in opposite directions to selectively engage said driving connections, a first pressure fluid actuated piston and cylinder device for shifting said clutch element in either direction, a driving connection between said spindle and said feed Shea including a feed clutch, a second pressure fluid actuated piston and cylinder device operable to engage said feed clutch whereby to cause rotation of said feed shaft at a feeding speed determined by the speed of the spindle, valve controlled means for supplying pressure fluid to said to said spindle, each of said drives including a pai r of alterable change gears and a clutch, pressure fluid actuated means for selectively engrging said clutches, a feed shaft 0 eratively connected to said supports, a driving connection between said spindle and said feed shaft for rotating said shaft at a feed speed including a feed clutch, pressure fluid actuated means for engaging said feed clut: 11, valve controlled means for supplying pressure fluid to said spindle clutch engaging means, a conduit for conducting pressure fluid from said spindle clutch engaging means to the feed clutch engaging means.

6. A lathe having, in combination, a bed, tool supports movably mounted thereon, a rotatably mounted headstock spindle, a prime mover, a feed shaft operatively connected to said supports, a driving connection between said prime mover and said spindle including a spindle clutch, a first pressure fluid actuated piston and cylinder device for engaging said clutch, a driving connection between said spindle and feed shaft including a feed clutch, a second pressure fluid actuated piston and cylinder device operable to engage said feed clutch, valve controlled means for supplying pressure fluid to said first device and a conduit extending from the cylinder of said first device to the cylinder of said second device and connected to the firstcylinder so as to delay operation of said second device until said first device has moved to engage the spindle clutch.

7. A lathe having, in combination, a bed, rotatable work supporting means, a plurality of movable tool supports carried by said bed, a plurality of similar cams mounted for-rotation about horizontal axes extending longitudinally of said bed,'all of said cams being mounted within the bed adjacent to one end thereof and having spiral cam grooves.

said cams for longitudinal sliding movement parallel to the cams, a follower carried b each member engaging the groove in the a j ac'ent cam, a plurality of connecting rods one extending longitudinally through each of said members and rotatable in said members in fixed longitudinal relation thereto, said rods being adapted at their outer ends for the application of a tool orhandle for rotating the rod, and an operative connection between each of said rods and one of said supports, including an element in screw threaded engagement with said rod whereby to permit of adjustment of said connection by rotation of said rod from the outside of said bed.

8. A lathe having, in combination, a bed, rotatable work supporting means, a plurality of movable tool supports carried by said bed, a plurality of similar cam drums mounted for rotation about horizontal axes extending longitudinally of said bed, all of said cams being mounted within the bed and adj acent to one end thereof and having spiral cam grooves therein with dwell portions at the ends of the grooves, a plurality of movable members, one mounted in said bed adjacent to each of said cams for longitudinal sliding movement parallel to the cams, a follower carried by each member engaging the groove in the adjacent cam, a connectin rod extending longitudinally through eac of said members and rotatable in said members in fixed longitudinal relation thereto, said rods being adapted at its outer end for the application of a tool or handle for rotating t e rod, said rods being operatively connected to said supports by means which ma be adjusted by rotation of said rods, an means for driving said cams including an adjustable connection with each of said cams to permit of variation of the angular relation of the cams to each other.

9. A lathe having, in combination, a bed, rotatable work supporting means, a movable tool support mounted on said bed, and means for actuating said support comprising a cam drum having a spiral groove therein and mounted in said bed adjacent one wall thereof nection between said member and said support, said means including a rod rotatably mounted in said member and projecting to the outside of said bed, said rod being operable upon rotation to adjust said connection.

10. A lathe having, in combination, a bed, rotatable work supporting means, a tool support movably mounted on said had, and means for actuating said support comprising a tubular cam drum having a spiral groove therein and supported in fixed longitudinal position in said bed adjacent to one wall thereof, means including a cam follower forming an operative connection between said cam and said support, a driving member rotatably supported in said bed coaxially with said drum, a sleeve extendingfrom the outside of said bed into said tubular cam drum and keyed to said drumso as to permit of longitudinal movement of the sleeve, said driving member and said sleeve having teeth formed thereon engageable by longitudinal move ment of said sleeve, andmeans acting between said driving member and said sleeve operable to hold said teeth in engaged relation, said means being releasable 'exteriorly of said bed so as to permit of angular adjustment of said cam and said driving member.

11. A lathe having, in combination, a bed, rotatable work supporting means, a movable tool support on said bed, and actuating means for said tool support comprising, a movable cam mounted in said bed, a member mounted for sliding movement through a wall of said bed, a follower fixed on said member and engaging said cam, and means forming an adjustab e operating connection between said member and said tool support, said means including a rod rotatably mounted in said member in fixed longitudinal relation thereto and projecting through said member to. the outside of said bed, said rod being operable upon rotation to adjust said connection.

12. A machine tool comprising, in combination, a bed, a movable support thereon, actuating means for said support, controlling means for said actuating means including a movable member having a plurality of operative positions arranged so that when said member is moved step by step from one extreme position to the other the support Wlll be moved through a cycle consisting of rapid approach, feed, and rapid return movements, said member having a neutral positios: located between its feed and rapid return positions, resilient means urging said member toward its rapid return position, a detent carried by and movable transversely with respect to said member, a control drum arranged to be moved in timed relation to said actuating means, said drum being of steplike form to provide a plurality of surfaces adapted for engagement by said detent to determine the operative position of said member, a plurality of trip dogs on said drum each operable to disengage said detent from one of said surfaces, so that said detent may be moved by said resilient means into engagement with anotherof said surfaces, and

i a cam device on said drum operable to engage said detent during rapid return movement of the support to move said member to its neutral position.

13. In a machine tool having a bed, a movable support thereon, actuating mechanism 

